CN109779998B - Torque distribution valve and wheel traveling hydraulic control system - Google Patents
Torque distribution valve and wheel traveling hydraulic control system Download PDFInfo
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- CN109779998B CN109779998B CN201711125413.2A CN201711125413A CN109779998B CN 109779998 B CN109779998 B CN 109779998B CN 201711125413 A CN201711125413 A CN 201711125413A CN 109779998 B CN109779998 B CN 109779998B
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- 238000013016 damping Methods 0.000 claims description 22
- 230000002093 peripheral effect Effects 0.000 claims description 7
- 239000007788 liquid Substances 0.000 claims description 6
- 230000006837 decompression Effects 0.000 claims description 5
- 230000000694 effects Effects 0.000 claims description 3
- 238000004891 communication Methods 0.000 abstract description 22
- 230000009471 action Effects 0.000 abstract description 6
- 239000003921 oil Substances 0.000 description 309
- 230000009467 reduction Effects 0.000 description 10
- 239000010720 hydraulic oil Substances 0.000 description 7
- 238000000926 separation method Methods 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 230000000149 penetrating effect Effects 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 230000005484 gravity Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
Abstract
The invention provides a torque distribution valve, which comprises a valve sleeve, a valve core and a return spring, wherein the valve core is accommodated in the valve sleeve, the return spring is accommodated in the valve sleeve, the valve core comprises a first end and a second end opposite to the first end, the return spring provides pretightening force for the second end of the valve core, the valve sleeve is provided with an oil return valve port, a pressure reducing/overflowing valve port and an oil inlet valve port, the pressure of the oil inlet valve port acts on the first end of the valve core after being reduced in proportion by the valve core, the pressure of the pressure reducing/overflowing valve port directly acts on the second end of the valve core by the valve core, the pressure of the pressure reducing/overflowing valve port is formed by oil entering the pressure reducing/overflowing valve port, and the communication relation among the oil return valve port, the pressure reducing/overflowing valve port and the oil inlet valve port is controlled under the action of the pressure received by the two ends, so that the pressure of the pressure reducing/overflowing valve port is equal to the pressure of the oil inlet valve port after being reduced in proportion by the valve core. The torque distribution valve can reasonably distribute oil. The invention also relates to a hydraulic control system for wheel walking.
Description
Technical Field
The invention relates to the technical field of hydraulic control, in particular to a torque distribution valve and a wheel traveling hydraulic control system.
Background
The self-walking type carrying equipment adopts two hydraulic motors which are connected in series to provide driving force for the driving wheels. When the self-walking type carrying equipment moves, the self-walking type carrying equipment is not only in straight walking, and needs to turn in necessary occasions, the turning radius of the left driving wheel is different from that of the right driving wheel during turning, and the rotating speed of the left motor driving the driving wheel is inconsistent with that of the right motor driving the right driving wheel. In the hydraulic control system, the hydraulic pressure firstly flows into the left motor and then flows into the right motor, when the vehicle turns left, the rotating speed of the left motor is smaller than that of the right motor, the hydraulic pressure cannot meet the requirement of the right motor, and the right motor can suck air, so that the right motor generates squeaking sounds; when the vehicle turns right, the hydraulic pressure that left side motor flowed out is far more than the suction volume of right motor, will form the holding pressure on left motor like this, seriously reduces right motor life-span.
As shown in fig. 1, in the prior art, in order to solve the problem of motor suction in a hydraulic system, a one-way oil compensating valve is usually connected between two motors, but the technical means cannot solve the problem of motor pressure holding.
As shown in fig. 2, in the prior art, in order to solve the problem of pressure holding of motors in a hydraulic system, an overflow valve is usually connected between two motors to reduce the pressure holding phenomenon, but the pressure of the overflow valve is fixed after being set, and cannot be changed along with the change of load, and a certain pressure holding is generated, so that the pressure holding cannot be completely eliminated.
Disclosure of Invention
Based on this, it is necessary to provide a torque distribution valve applied in a hydraulic control system for wheel traveling to solve the problem of pressure holding and suction occurring when two motors are connected in series.
The invention provides a valve which is characterized in that the pressure of an oil inlet valve port is subjected to valve core proportion pressure reduction and acts on a first end of the valve core, the pressure of the pressure reduction/overflow valve port is subjected to valve core proportion pressure reduction and acts on a second end of the valve core, the pressure of the pressure reduction/overflow valve port is formed by the fact that oil of the oil inlet valve port is subjected to valve core proportion pressure reduction and then enters the pressure reduction/overflow valve port, the pressure acting area of the first end and the pressure acting area of the second end of the valve core are the same, the valve core controls the communication relation among the oil return valve port, the pressure reduction/overflow valve port and the oil inlet valve port under the action of pressure of two ends, and the pressure of the pressure reduction/overflow valve port is equal to the pressure of the oil inlet valve port subjected to valve core proportion pressure reduction and acts on the first end of the valve core.
Further, the valve sleeve is provided with a control cavity with pressure acting on the first end of the valve core and a feedback cavity with pressure acting on the second end of the valve core, a first oil duct communicated with the oil inlet valve port and a second oil duct communicated with the pressure reducing/overflowing valve port and the feedback cavity are arranged in the valve core, the first end of the valve core is provided with a first damping hole communicated with the first oil duct and the control cavity, and a second damping hole communicated with the control cavity and the oil return valve port is further arranged on the valve sleeve.
Further, the liquid resistance of the first damping hole is equal to that of the second damping hole.
Further, the peripheral wall of the valve core is provided with a first oil groove, the first oil groove extends towards the two ends of the valve core along the axial direction of the valve core, the first oil groove is communicated with the second oil duct, the first oil groove is communicated with the pressure reducing/overflow valve port, the pressure reducing/overflow valve port is communicated with the oil return valve port and the oil inlet valve port through the first oil groove, the valve core controls the conduction and the separation of the first oil groove and the oil return valve port under the action of pressure at the two ends, and controls the conduction and the separation of the first oil groove and the oil inlet valve port.
Further, a second oil groove is further formed in the peripheral wall of the valve core, the second oil groove and the first oil groove are arranged at intervals in the axial direction of the valve core, and the first oil duct is communicated with the oil inlet valve port through the second oil groove.
Further, a throttle plug is arranged at the first end of the valve core, and the first damping hole is formed in the throttle plug.
Further, a filter screen is arranged in the first oil duct.
The invention also provides a wheel walking hydraulic control system, which comprises:
the three-way four-position electromagnetic directional valve is used for controlling the advancing and retreating of the self-walking type carrying equipment and comprises a main oil inlet, a main oil return port, a working oil inlet and a working oil return port, wherein the main oil inlet of the three-way four-position electromagnetic directional valve is connected with a hydraulic pump, and the main oil return port of the three-way four-position electromagnetic directional valve is connected with an oil tank;
the first motor is connected with a working oil inlet of the three-way four-position electromagnetic reversing valve, and the second motor is connected with a working oil return port of the three-way four-position electromagnetic reversing valve;
the shuttle valve comprises a first oil inlet, a second oil inlet and an oil outlet, the first oil inlet of the shuttle valve is connected with a working oil inlet of the three-way four-position electromagnetic reversing valve, and the second oil inlet of the shuttle valve is connected with a working oil return port of the three-way four-position electromagnetic reversing valve;
in the torque distribution valve, the oil inlet valve port is connected with the oil outlet of the shuttle valve, the oil return valve port is connected with the oil tank, and the pressure reducing/overflow valve port is connected between the first motor and the second motor.
Further, the three-way four-way electromagnetic reversing valve further comprises a two-position four-way electromagnetic reversing valve, the two-position four-way electromagnetic reversing valve comprises a main oil inlet, a main oil return port, a working oil inlet and a working oil return port, wherein the main oil inlet of the two-position four-way electromagnetic reversing valve is connected with the working oil return port of the three-way four-way electromagnetic reversing valve, the working oil return port of the two-position four-way electromagnetic reversing valve is connected with the working oil inlet of the three-way four-way electromagnetic reversing valve, one end of the first motor is connected with the working oil inlet of the two-position four-way electromagnetic reversing valve, one end of the second motor is connected with the main oil return port of the two-position four-way electromagnetic reversing valve, the other end of the second motor is connected onto the working oil return port of the three-way four-way electromagnetic reversing valve, and when the two-position four-way electromagnetic reversing valve is powered off, the first motor is connected with the second motor in series.
Further, the motor driving device further comprises a two-position two-way electromagnetic valve, wherein the two-position two-way electromagnetic valve is connected between one end of the second motor and the pressure reducing/overflow valve port of the torque distribution valve, when the two-position two-way electromagnetic valve and the two-position four-way electromagnetic reversing valve are electrified simultaneously, the first motor is connected with the second motor in parallel, the two-position two-way electromagnetic valve is closed, and the connection between the pressure reducing/overflow valve port of the torque distribution valve and one end of the second motor is disconnected.
By applying the technical scheme, compared with the prior art, the invention has the following advantages:
according to the torque distribution valve and the wheel traveling hydraulic control system, the communication relation between the pressure reducing/overflow valve port and the oil inlet valve port and the opening and closing of the oil return valve port can be adjusted according to the pressure change of the pressure reducing/overflow valve port, when the pressure reducing/overflow valve port is enlarged, the communication between the pressure reducing/overflow valve port and the oil inlet valve port is blocked, the oil return valve port is opened, oil in the pressure reducing/overflow valve port flows back to the oil tank through the oil return valve port, the communication area between the pressure reducing/overflow valve port and the oil inlet valve port is increased in the pressure reducing/overflow valve port, and meanwhile, the oil return valve port is closed, so that the oil in the oil inlet valve port provides oil for an external system through the pressure reducing/overflow valve port, and the torque distribution is realized.
Drawings
Fig. 1 and 2 are prior art wheel travel hydraulic control systems.
Fig. 3 is a schematic view of the structure of the torque distribution valve of the present invention.
Fig. 4 is a functional schematic diagram of the torque distribution valve of the present invention.
Fig. 5 and 6 are schematic views of the torque distribution principle of the torque distribution valve of the present invention.
Fig. 7 is an enlarged view of V in fig. 6.
Fig. 8 is a pressure distribution schematic diagram of a control chamber in the torque distribution valve of the present invention.
Fig. 9 is a schematic structural view of a wheel travel hydraulic control system according to a first embodiment of the present invention.
Fig. 10 is a schematic structural view of a wheel travel hydraulic control system according to a second embodiment of the present invention.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are some, but not all embodiments of the invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
Referring to fig. 3-6 in combination, the present invention provides a torque distribution valve 100, which includes a valve housing 1, a valve core 2 accommodated in the valve housing 1, and a return spring 3 accommodated in the valve housing 1. The valve core 2 comprises a first end and a second end opposite to the first end, and the return spring 3 provides pretightening force for the second end of the valve core 2. The valve sleeve 1 is provided with an oil return valve port B1, a pressure reducing/overflowing valve port C1 and an oil inlet valve port A1, the pressure of the oil inlet valve port A1 acts on the first end of the valve core 2 after being reduced in proportion by the valve core, the pressure of the pressure reducing/overflowing valve port C1 directly acts on the second end of the valve core 2 by the valve core, and the pressure of the pressure reducing/overflowing valve port C1 is formed by the fact that the oil of the oil inlet valve port A1 enters the pressure reducing/overflowing valve port C1 after being reduced in proportion by the valve core. The pressure acting areas of the first end and the second end of the valve core 2 are the same, and the valve core 2 controls the communication relation among the oil return valve port B1, the pressure reducing/overflowing valve port C1 and the oil inlet valve port A1 under the action of the pressure of the two ends, so that the pressure of the pressure reducing/overflowing valve port C1 is equal to the pressure of the oil inlet valve port A1 acting on the first end of the valve core 2 through the valve core proportion pressure reduction.
It will be appreciated that although the pressure of the relief/overflow port C1 is formed by the oil of the oil inlet port A1 entering the relief/overflow port C1, when the torque distribution valve 100 is applied to the hydraulic system, if the hydraulic driving portion in the hydraulic system needs to be supplied with more oil, the pressure of the relief/overflow port C1 is suddenly increased under the influence of the external oil pressure, at this time, the pressure of the second end of the valve core 2 is increased, the valve core 2 moves in the direction of the first end of the valve core 2, so that the communication area between the oil inlet port A1 and the relief/overflow port C1 is reduced or both are directly blocked, the relief/overflow port C1 is communicated with the oil return port B1, the oil return port B1 is opened, the redundant oil in the hydraulic system enters the oil return port B1 through the relief/overflow port C1, and then the oil return tank is returned through the oil return port B1, and the pressure of the relief/overflow port C1 is reduced, so that the pressure of the relief/overflow port C1 is equal to the pressure of the oil inlet port A1 after the pressure is proportionally reduced through the valve core 2. Conversely, if the hydraulic driving part in the hydraulic system needs less supply and demand of oil, the pressure of the pressure reducing/overflowing valve port C1 is suddenly reduced under the influence of external oil pressure, at this time, the pressure of the second end of the valve core 2 is reduced, the valve core 2 moves towards the direction of the second end of the valve core 2, so that the oil inlet port A1 is communicated with the pressure reducing/overflowing valve port C1 or the communication area is increased, and meanwhile, the communication area between the pressure reducing/overflowing valve port C1 and the oil return valve port B1 is reduced, or the oil return valve port B1 is closed, more oil entering the pressure reducing/overflowing valve port C1 is output outwards, and at the same time, the pressure of the pressure reducing/overflowing valve port C1 is increased, so that the pressure of the pressure reducing/overflowing valve port C1 is equal to the pressure of the oil inlet valve port A1 after the pressure of the pressure reducing valve core 2 is reduced in proportion.
In this embodiment, when the torque distribution valve 100 of the present invention is not connected to oil pressure, that is, when the torque distribution valve 100 is in an initial state, the valve core 2 opens the oil return valve port B1 under the pre-tightening force of the return spring 3, and the pressure reducing/overflow valve port C1 is connected to the oil return valve port B1, and at the same time, the pressure reducing/overflow valve port C1 is separated from the oil inlet valve port A1, that is, no oil can flow between the pressure reducing/overflow valve port C1 and the oil inlet valve port A1. It should be noted that, the stiffness of the return spring 3 is smaller, the compression force just can resist the gravity of the valve core 2, the installation direction of the valve core 2 is avoided from affecting the position of the valve core 2, and meanwhile, the compression force of the return spring 3 is far smaller than the force generated by the hydraulic pressure of the oil on the acting area of the valve core 2, so that the return spring 3 only plays a role in return, and the further compression force is negligible.
Specifically, the valve housing 1 includes a first end and a second end opposite to the first end, and the oil return port B1, the pressure reducing/relief port C1, and the oil intake port A1 are sequentially disposed between the first end of the valve housing 1 and the second end of the valve housing 1. The valve housing 1 is provided with a control chamber 11 with pressure acting on the first end of the valve core 2 and a feedback chamber 12 with pressure acting on the second end of the valve core 2, preferably the first end of the control chamber 11 is arranged on the valve housing 1, the feedback chamber 12 is arranged on the second end of the valve housing 1, the first end of the valve core 2 is accommodated in the control chamber 11, the pressure of the control chamber 11 acts on the first end of the valve core 2, the second end of the valve core 2 is accommodated in the feedback chamber 12, and the pressure of the feedback chamber 11 acts on the second end of the valve core 11. The valve core 2 is internally provided with a first oil passage 21 communicated with the oil inlet valve port A1 and a second oil passage 22 communicated with the pressure reducing/overflow valve port C1 and the feedback cavity 12, and the first end of the valve core 2 is provided with a first damping hole 23 communicated with the first oil passage 21 and the control cavity 11. The valve sleeve 2 is also provided with a second damping hole 13 which is communicated with the control cavity 11 and is communicated with the oil return valve port B1. By such arrangement, the pressure of the oil inlet valve port A1 can be enabled to be acted on the first end of the valve core 2 through the decompression action of a certain proportion, the pressure of the decompression/overflow valve port C1 is directly acted on the second end of the valve core 2, the decompression proportion of the oil inlet valve port A1 can be determined according to the theoretical knowledge of liquid resistance, the oil enters the first oil duct 21 through the oil inlet valve port A1, then enters the control cavity 11 through the first damping hole 23, meanwhile, the oil also returns to the oil return valve port B1 through the second damping hole 13,then, the oil is returned, in this process, as shown in fig. 8, the first damping hole 23, the second damping hole 13 and the control chamber 11 form a hydraulic half-bridge, and the hydraulic resistances of the first damping hole 23 and the second damping hole 13 are respectively assumed to be R 1 、R 2 The pressure of the control chamber 11 is P K Then, according to the theoretical knowledge of the liquid resistance, the following steps are obtained: p (P) K ＝P L ×R 1 2 /R 1 2 +R 2 2 At R 1 And R is R 2 After the value of (1) is determined, the internal pressure P of the first oil passage 21 L The pressure of the control chamber 11 is the same as that of the oil inlet valve A1, the proportion relation between the pressure in the control chamber 11 and the pressure of the oil inlet valve A1 can be determined, and P K With P L Is varied by variation of (1), if R 1 ＝R 2 Then the pressure P of the relief/overflow port C1 K The pressure of the oil inlet valve port A1 is equal to half of the pressure of the oil inlet valve port A1, namely, the pressure of the oil inlet valve port A1 is reduced by half through the valve core 2 and then acts on the first end of the valve core 2.
In the present embodiment, the liquid resistances of the first damping hole 23 and the second damping hole 13 are equal, and the pressure of the oil inlet port A1 is reduced by half through the valve spool 2 and then acts on the first end of the valve spool 2, and at the same time, the pressure of the pressure reducing/overflowing port C1 is made equal to half the pressure of the oil inlet port A1. In other embodiments, the liquid resistances of the first damping hole 23 and the second damping hole 13 may be different.
In this embodiment, the peripheral wall of the valve core 2 is provided with a first oil groove 24, the first oil groove 24 extends towards two ends of the valve core 2 along the axial direction of the valve core 2, the first oil groove 24 is communicated with a second oil duct 22, the first oil groove 24 is communicated with a pressure reducing/overflowing valve port C1, the pressure reducing/overflowing valve port C1 is communicated with an oil return valve port B1 and an oil inlet valve port A1 through the first oil groove 24, the valve core 2 controls the conduction and the separation of the first oil groove 24 and the oil return valve port B1 under the action of pressure at two ends, and controls the conduction and the separation of the first oil groove 24 and the oil inlet valve port A1. Specifically, the first oil groove 24 includes a first end and a second end opposite to the first end, the first end of the first oil groove 24 is used for communicating with the oil return port B1, the second end of the first oil groove 24 is used for communicating with the pressure reducing/overflowing port C1, in an initial state of the torque distribution valve 100, that is, when the torque distribution valve 100 does not flow in oil, the restoring spring 3 pre-biases the valve core 2, the first end of the first oil groove 24 faces the oil return port B1, the oil return port B1 is opened, the second end of the first oil groove 24 is located at the outer side of one side of the oil inlet port A1 near the pressure reducing/overflowing port C1, the valve core 2 blocks the first oil groove 24 from the oil inlet port A1, so that the pressure reducing/overflowing port C1 is blocked from the oil inlet port A1, when the pressure applied to the first end of the valve core 2 is greater than the pressure applied to the second end, the valve core 2 moves toward the direction where the second end of the valve core 2 is located, when the second end of the first oil groove 24 moves to face the oil inlet port A1 along with the valve core 2, the first oil groove 24 is communicated with the oil inlet port A1, at this time, the first oil groove 24 forms a relief port a11 (as shown in fig. 7) communicated with the first oil groove 24, and as the valve core 2 moves, the area of the first oil groove 24 facing the oil inlet port A1 is larger and larger, namely the flow area of the relief port a11 is larger and larger, while the first end of the first oil groove 24 moves to the direction of the second end of the valve core 2 along with the valve core 2, the facing area of the first end of the first oil groove 24 and the oil return port B1 is smaller and smaller until the first end of the first oil groove 24 moves to the outer side of the oil return port B1, which is close to the relief/overflow port C1, the valve core 2 blocks the oil return port B1 from the first oil groove 24, and the oil return port B1 is closed. The moving direction of the valve core 2 is opposite, the flow area of the pressure reducing valve port a11 gradually becomes smaller until the valve core 2 blocks the communication between the first oil groove 24 and the oil inlet valve port A1, and meanwhile, the oil return valve port B1 is communicated with the first end of the first oil groove 24, and the communication area is larger and larger. In the present embodiment, the first oil groove 24 is an annular groove that opens around the peripheral wall of the valve spool 2 so that the first oil groove 24 can communicate with the relief/overflow valve port C1 easily when the valve spool 2 is installed. In this example, the second oil passage 22 is provided along the axial direction of the spool 2, and one end of the second oil passage 22 remote from the second end of the spool 2 is provided with, for example, an oil guide hole 220 penetrating through the spool 2 to realize communication of the second oil passage 22 with the first oil groove 25.
In the present embodiment, the peripheral wall of the valve element 2 is further provided with a second oil groove 25, and in the axial direction of the valve element 2, the second oil groove 25 is provided at an interval from the first oil groove 24, and the first oil passage 21 communicates with the oil intake port A1 through the second oil groove 25 to prevent oil leakage. In this example, the first oil passage 21 is provided along the axial direction of the valve spool 2, and one end thereof is provided with an oil guide hole penetrating the peripheral wall of the valve spool 1, through which the first oil passage 21 communicates with the second oil groove 25. The second oil groove 25 is preferably an annular groove.
In the present embodiment, the first end of the spool 2 is provided with a throttle plug 26, and the first orifice 23 is provided on the throttle plug 26.
Further, a filter screen 27 is disposed in the first oil passage 21 to filter the hydraulic oil in the oil intake first oil passage 21.
It should be noted that, the torque distribution valve 100 of the present invention further includes a valve cover 110, the valve cover 110 is installed at one end of the valve sleeve 1 provided with the control chamber 11, the two ends of the valve sleeve 1 are further provided with valve sleeve sealing seats, and the valve sleeve sealing seats function and installation mode are all common techniques in the art, and are not described herein.
After being connected into a hydraulic circuit, the torque distribution valve 100 of the invention is characterized in that oil enters the first oil duct 21 through the oil inlet valve port A1, is filtered through the filter screen 27, then enters the control cavity 11 through the first damping hole 23, and simultaneously returns to the oil return valve port B1 through the second damping hole 13, and then returns to the oil tank. Since no throttle is passed between the first oil passage 21 and the oil intake port A1, the internal pressure P of the first oil passage 21 L The pressure of the oil inlet valve port A1 is the same as that of the oil inlet valve port A1, namely, the pressure of the oil inlet valve port A1 is reduced to P after entering the control cavity 11 K Acting on the first end of the spool 2, at which point the pressure P K The valve core 2 is pushed to move towards the direction of the second end of the valve core 2 and simultaneously compresses the return spring 3, and at the moment, the valve core 2 does not block the communication between the oil inlet valve port A1 and the pressure reducing/overflow valve port C1 any more. When the pressure reducing/relief valve port C1 communicates with the oil intake valve port A1, the pressure reducing/relief valve port C1 communicates with a pressure reducing valve port a11 formed in the oil intake valve port A1.
The oil in the oil inlet valve port A1 enters the first oil groove 24 through the pressure reducing valve port A11 and enters the pressure reducing/overflow valve port C1, the pressure entering the pressure reducing/overflow valve port C1 will drop due to the throttling effect of the pressure reducing valve port A11, the oil in the first oil groove 24 enters the feedback cavity 12 through the second oil duct 22, after the oil pressure is built in the feedback cavity 12, the pressure in the feedback cavity 12 is P S Since the second oil passage 22 has no throttling effect, the pressure P of the feedback chamber 12 S Equal to the pressure at the relief/overflow port C1, i.e. reliefThe pressure of the relief valve opening C1 acts on the second end of the valve element 2. When the oil pressure in the feedback chamber 12 has just built up, the pressure P in the control chamber 11 K Greater than the pressure P of the feedback chamber 12 S The valve core 2 will move downwards continuously, the flow area of the relief valve port A11 will increase, the pressure of the relief/overflow valve port C1 will increase along with the increase of the flow area of the relief valve port A11, the pressure of the relief/overflow valve port C1 is transferred to the feedback chamber, so that the pressure P of the feedback chamber 12 S Also gradually increase until P S ＝P K At this time, the valve core 2 is not moving to a certain position, and the pressure of the pressure reducing/relief valve port C1 is equal to the pressure P of the control chamber 11 K . After the pressure balance is established, when some external factor causes the pressure of the pressure reducing/relief valve port C1 to suddenly increase by more than the pressure P of the control chamber 11 K When the pressure of the relief/overflow port C1 is immediately transferred to the feedback chamber 12, i.e. P S ＞P K At this time, the valve core 2 will move toward the direction of the first end of the valve core 2 to close the pressure reducing valve port a11, that is, the valve core 2 will block the communication between the pressure reducing/overflowing valve port C1 and the oil inlet valve port A1, and simultaneously open the oil return valve port B1, part of the oil in the pressure reducing/overflowing valve port C1 overflows the oil return valve port B1 to return to the oil tank, the pressure of the pressure reducing/overflowing valve port C1 is reduced until the pressure of the pressure reducing/overflowing valve port C1 is equal to the pressure P of the control chamber 11 K 。
Of course, after the pressure balance is established, when some external factor causes the pressure of the pressure reducing/relief valve port C1 to be suddenly smaller than P K When the pressure of the relief/overflow port C1 is immediately transferred to the feedback chamber 12, i.e. P S <P K At this time, the valve core 2 will move toward the direction of the second end of the valve core 2 to close the oil return valve port B1 and increase the flow area of the relief valve port a11 to increase the pressure P of the relief/overflow valve port C1 3 Until the pressure of the relief/overflow port C1 is equal to the pressure P of the control chamber 11 K At the same time, the oil inlet port A1 will have more oil distributed to the relief/overflow port C1.
Therefore, the torque distribution valve can enable the pressure of the pressure reducing/overflowing valve port C1 to be equal to the pressure of the control cavity 11, the ratio of the pressure of the control cavity 11 to the pressure of the oil inlet valve port A1 is constant, so that the ratio of the pressure reducing/overflowing valve port C1 to the pressure of the oil inlet valve port A1 is constant, when the pressure reducing/overflowing valve port C1 is influenced by external factors, the communication area between the oil inlet valve port A1 and the pressure reducing/overflowing valve port C1 can be changed, the opening and closing of the oil return valve port B1 are controlled, and when the pressure of the pressure reducing/overflowing valve port C1 is reduced, namely, when an external system needs more oil, the communication area between the oil inlet valve port A1 and the pressure reducing/overflowing valve port C1 is increased, and the oil return valve port B1 is closed, so that more hydraulic pressure in the oil inlet valve port A1 is supplied to the external system; when the pressure of the pressure reducing/overflowing valve port C1 is increased, that is, the oil supply of an external system is greater than required, the communication between the oil inlet valve port A1 and the pressure reducing/overflowing valve port C1 is blocked, the oil return valve port B1 is opened, so that the oil of the external system returns to the oil return valve port B1 through the pressure reducing/overflowing valve port C1, and then the oil tank is filled.
The invention also provides a wheel traveling hydraulic control system with the torque distribution valve 100, which is used in self-traveling type carrying equipment and is used for providing driving force for driving wheels of the equipment. After the torque distribution valve 100 is applied, the torque distribution valve 100 can effectively prevent the motor from generating suction and holding pressure.
As shown in fig. 8, the wheel traveling hydraulic control system of the first embodiment of the invention includes: a three-way four-position electromagnetic directional valve 4, a shuttle valve 5, the torque distribution valve 100 described above, a first motor 6, and a second motor 7.
The three-way four-position electromagnetic directional valve 4 is used for controlling the forward and backward movement of the self-walking type carrying equipment and comprises a main oil inlet P2, a main oil return port T2, a working oil inlet A2 and a working oil return port B2, wherein the main oil inlet P2 is connected to the hydraulic pump, and the main oil return port T2 is connected with the oil tank. When the coil on the left side of the three-way four-position electromagnetic directional valve 4 is powered on, the self-walking type carrying equipment advances, and when the coil on the right side of the three-way four-position electromagnetic directional valve 4 is powered on, the self-walking type carrying equipment retreats.
The first motor 6 and the second motor 7 connected in series with the first motor 6, the first motor 6 is connected with the working oil inlet A2, and the second motor 7 is connected with the working oil return port B2. In the present embodiment, the first motor 6 is used to drive the left-hand wheel of the apparatus and the second motor 7 is used to drive the right-hand wheel of the apparatus.
The shuttle valve 5 comprises a first oil inlet A3, an oil outlet B3 and a second oil inlet C3, wherein the first oil inlet A3 is connected with the working oil inlet A2, and the second oil inlet C3 is connected with the working oil return port B2.
The oil intake port A1 and the oil outlet port B3 of the torque distribution valve 100 are connected, the oil return port B1 and the oil tank are connected, and the pressure reducing/relief port C1 is connected between the first motor 6 and the second motor 7.
When the wheel traveling hydraulic control system is used, when the left electromagnet of the three-way four-position electromagnetic directional valve 4 is powered on, the self-traveling type conveying equipment forwards travels, the working oil inlet A2 of the three-way four-position electromagnetic directional valve 4 is used as a hydraulic oil outlet, hydraulic oil firstly enters the first motor 6 and then flows into the second motor 7 through the first motor 6; meanwhile, oil output by the working oil inlet A2 of the three-way four-position electromagnetic directional valve 4 also enters an oil inlet valve port A1 of the torque distribution valve 100 through a first oil inlet A3 of the shuttle valve 5, oil pressure is built in the torque distribution valve 100, the pressure of the pressure reducing/overflowing valve port C1 is equal to half of the pressure of the oil inlet valve port A1 and half of the pressure of the working oil inlet A2, the rotation speed of the vehicle in a non-turning state is the same between the first motor 6 and the second motor 7, the pressure between the first motor 6 and the second motor 7 is equal to half of the pressure of the working oil inlet A2, and the whole system is in a pressure balance state.
As shown in fig. 8, when the apparatus turns left, the rotation speed of the left wheel of the apparatus is lower than the rotation speed of the right wheel of the apparatus, that is, the rotation speed of the first motor 6 needs to be lower than the rotation speed of the second motor 7, at this time, the second motor 7 has the function of a hydraulic pump to start to absorb hydraulic oil, so that the pressure in the middle of the two motors becomes smaller and lower, that is, the pressure of the pressure reducing/overflowing valve port C1 of the torque distribution valve 100 becomes smaller, at this time, the pressure of the pressure reducing/overflowing valve port C1 is smaller than the pressure of the control chamber 11, the torque distribution valve 100 starts to act, the valve core 2 moves in the direction where the second end of the valve core 2 is located, the communication area between the pressure reducing/overflowing valve port C1 and the oil inlet port A1 increases until the pressure of the pressure reducing/overflowing valve port C1 is the same as the pressure of the control chamber 11, at the same time, the oil returning valve port B1 is closed, and the oil entering the oil inlet port A1 is replenished between the two motors, so as to prevent the second motor 7 from idling. When the vehicle turns right in the running process, the first motor 6 is directly supplied with oil from the working oil inlet A2, at this time, the left wheel is a driving wheel, the right wheel is a driven wheel, the rotation speed of the first motor 6 is faster than that of the second motor 7, hydraulic oil flowing out of the first motor 6 is larger than that of hydraulic oil required to be sucked by the second motor 7, so that the pressure between the two motors, namely the pressure of the pressure reducing/overflow valve port C1 of the torque distribution valve 100, becomes higher, at this time, the pressure of the pressure reducing/overflow valve port C1 is larger than that of the control cavity 11, the torque distribution valve 100 starts to act, the valve core 2 moves towards the direction of the first end of the valve core 2, the communication area between the pressure reducing/overflow valve port C1 and the oil inlet valve port A1 is reduced until the valve core 2 blocks the pressure reducing/overflow valve port C1 from the oil inlet valve port A1, meanwhile, the oil return valve port B1 is opened, redundant oil between the two motors enters the oil return port B1 through the pressure reducing/overflow valve port C1, and finally returns to the oil tank, and thus the pressure between the two motors is prevented.
When the electromagnet at the right side of the three-way four-position electromagnetic directional valve 4 is powered on, the self-walking type carrying equipment runs backwards, the working oil return port B2 outputs hydraulic oil, and when the self-walking type carrying equipment rotates left and right, the control mode of the wheel walking hydraulic control system is opposite to the control mode of the forward running of the self-walking type carrying equipment, and the description is omitted here; accordingly, the shuttle valve 5 selects the operation sequence of the high pressure oil passing through the torque distribution valve 100 according to the pressure.
As shown in fig. 9, the basic structure and principle of the wheel traveling hydraulic control system of the second embodiment of the invention are basically the same as those of the first embodiment, and the wheel traveling hydraulic control system of the second embodiment of the invention is different from the first embodiment in that it further includes a two-position four-way electromagnetic directional valve 8, the two motors are connected through the two-position four-way electromagnetic directional valve 8, and the two motors are connected in series when the two-position four-way electromagnetic directional valve 8 is powered off.
Specifically, the two-position four-way electromagnetic directional valve 8 includes a main oil inlet P4, a main oil return port T4, a working oil inlet A4 and a working oil return port B4, wherein the main oil inlet P4 of the two-position four-way electromagnetic directional valve 8 is connected with the working oil return port B2 of the three-way four-position electromagnetic directional valve 4, the working oil return port B4 of the two-position four-way electromagnetic directional valve 8 is connected with the working oil inlet A2 of the three-way four-way electromagnetic directional valve 4, one end of the first motor 6 is connected with the working oil inlet A4 of the two-position four-way electromagnetic directional valve 8, one end of the second motor 7 is connected with the pressure reducing/overflow valve port C1 of the torque distribution valve 100, one end of the second motor 7 is also connected with the main oil return port T4 of the two-position four-way electromagnetic directional valve 8, and the other end of the second motor 7 is connected on the working oil return port B2 of the three-way four-way electromagnetic directional valve 4, so that when the two-position four-way electromagnetic directional valve 8 is powered off, the connection can realize that the first motor 6 and the second motor 7 are connected in series.
The wheel traveling hydraulic control system according to the second embodiment of the present invention further includes a two-position two-way solenoid valve 9, wherein the two-position two-way solenoid valve 9 is connected between one end of the second motor 7 and the pressure reducing/overflow valve port C1 of the torque distribution valve 100, when the two-position two-way solenoid valve 9 and the two-position four-way solenoid directional valve 8 are simultaneously electrified, the first motor 6 and the second motor 7 are connected in parallel, the two-position two-way solenoid valve 9 is closed, the connection between the pressure reducing/overflow valve port C1 of the torque distribution valve 100 and one end of the second motor 7 is disconnected, the system is at a low speed, the two-side motors distribute flow according to different hydraulic resistances as required, at this time, the torque distribution valve is not required to distribute flow, and at this time, high-low speed switching of the traveling system is realized.
In summary, the torque distribution valve 100 and the wheel traveling hydraulic control system according to the present invention can adjust the communication relationship between the pressure reducing/relief valve port C1 and the oil inlet valve port A1 and the opening/closing of the oil return valve port B1 according to the pressure change of the pressure reducing/relief valve port C1, and when the pressure reducing/relief valve port C1 becomes large, the communication between the pressure reducing/relief valve port C1 and the oil inlet valve port A1 is blocked, the oil return valve port B1 is opened, the oil in the pressure reducing/relief valve port C1 flows back to the oil tank through the oil return valve port B1, the communication area between the pressure reducing/relief valve port C1 and the oil inlet valve port A1 is increased at the pressure reducing/relief valve port C1, and the oil return valve port B1 is closed, so that the oil in the oil inlet valve port A1 supplies the oil to the external system through the pressure reducing/relief valve port C1, thereby realizing the torque distribution.
The technical features of the above-described embodiments may be arbitrarily combined, and all possible combinations of the technical features in the above-described embodiments are not described for brevity of description, however, as long as there is no contradiction between the combinations of the technical features, they should be considered as the scope of the description.
The above examples illustrate only a few embodiments of the invention, which are described in detail and are not to be construed as limiting the scope of the invention. It should be noted that it will be apparent to those skilled in the art that several variations and modifications can be made without departing from the spirit of the invention, which are all within the scope of the invention. Accordingly, the scope of protection of the present invention is to be determined by the appended claims.
Claims (9)
1. The torque distribution valve comprises a valve sleeve, a valve core and a return spring, wherein the valve core is accommodated in the valve sleeve, the return spring is accommodated in the valve sleeve, the valve core comprises a first end and a second end opposite to the first end, the return spring provides pretightening force for the second end of the valve core, the valve sleeve is provided with an oil return valve port, a pressure reducing/overflow valve port and an oil inlet valve port.
2. The torque distribution valve according to claim 1, characterized in that: the liquid resistance of the first damping hole is equal to that of the second damping hole.
3. The torque distribution valve according to claim 1, characterized in that: the peripheral wall of case is equipped with first oil groove, first oil groove is along the axial of case extends to the both ends of case, first oil groove with second oil duct intercommunication, first oil groove with decompression/overflow valve port intercommunication, decompression/overflow valve port passes through first oil groove with oil return valve port and oil feed valve port intercommunication, the case is under the effect of both ends pressure control first oil groove with the switch-on and the cut-off of oil return valve port, and control first oil groove with the switch-on and the cut-off of oil feed valve port.
4. A torque distribution valve according to claim 3, characterized in that: the periphery wall of case still is equipped with the second oil groove in the axial of case, the second oil groove with first oil groove interval sets up, first oil duct passes through the second oil groove with advance oil valve port intercommunication.
5. The torque distribution valve according to claim 1, characterized in that: the first end of the valve core is provided with a throttle plug, and the first damping hole is formed in the throttle plug.
6. The torque distribution valve according to claim 1, characterized in that: a filter screen is arranged in the first oil duct.
7. A wheel travel hydraulic control system, comprising:
the three-way four-position electromagnetic directional valve is used for controlling the advancing and retreating of the self-walking type carrying equipment and comprises a main oil inlet, a main oil return port, a working oil inlet and a working oil return port, wherein the main oil inlet of the three-way four-position electromagnetic directional valve is connected with a hydraulic pump, and the main oil return port of the three-way four-position electromagnetic directional valve is connected with an oil tank;
the first motor is connected with a working oil inlet of the three-way four-position electromagnetic reversing valve, and the second motor is connected with a working oil return port of the three-way four-position electromagnetic reversing valve;
the shuttle valve comprises a first oil inlet, a second oil inlet and an oil outlet, the first oil inlet of the shuttle valve is connected with a working oil inlet of the three-way four-position electromagnetic reversing valve, and the second oil inlet of the shuttle valve is connected with a working oil return port of the three-way four-position electromagnetic reversing valve;
the torque distribution valve of any of claims 1-6, the oil inlet port being connected to an oil outlet of the shuttle valve, the oil return port being connected to an oil tank, the relief/overflow port being connected between the first motor and the second motor.
8. The wheel travel hydraulic control system according to claim 7, characterized in that: the four-way electromagnetic reversing valve comprises a torque distribution valve, and is characterized by further comprising a two-position four-way electromagnetic reversing valve, wherein the two-position four-way electromagnetic reversing valve comprises a main oil inlet, a main oil return port, a working oil inlet and a working oil return port, the main oil inlet of the two-position four-way electromagnetic reversing valve is connected with the working oil return port of the three-way four-way electromagnetic reversing valve, one end of a first motor is connected with the working oil inlet of the three-way four-way electromagnetic reversing valve, the other end of the first motor is connected with the working oil inlet of the two-position four-way electromagnetic reversing valve, one end of a second motor is connected with the main oil return port of the two-position four-way electromagnetic reversing valve, the other end of the second motor is connected to the working oil return port of the three-way four-way electromagnetic reversing valve, and when the two-position four-way electromagnetic reversing valve is powered off, the first motor is connected with the second motor in series.
9. The wheel travel hydraulic control system according to claim 8, characterized in that: the motor is characterized by further comprising a two-position two-way electromagnetic valve, wherein the two-position two-way electromagnetic valve is connected between one end of the second motor and a pressure reducing/overflow valve port of the torque distribution valve, when the two-position two-way electromagnetic valve and the two-position four-way electromagnetic reversing valve are electrified simultaneously, the first motor is connected with the second motor in parallel, the two-position two-way electromagnetic valve is closed, and the connection between the pressure reducing/overflow valve port of the torque distribution valve and one end of the second motor is disconnected.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201711125413.2A CN109779998B (en) | 2017-11-14 | 2017-11-14 | Torque distribution valve and wheel traveling hydraulic control system |
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| CN201711125413.2A CN109779998B (en) | 2017-11-14 | 2017-11-14 | Torque distribution valve and wheel traveling hydraulic control system |
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| CN109779998A CN109779998A (en) | 2019-05-21 |
| CN109779998B true CN109779998B (en) | 2023-11-24 |
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| CN112343879A (en) * | 2020-10-29 | 2021-02-09 | 武汉船用机械有限责任公司 | Same-pressure-difference rotary motor control system |
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| GB1309162A (en) * | 1969-06-28 | 1973-03-07 | Bosch Gmbh Robert | Fluid flow-regulating valves |
| CN101392774A (en) * | 2008-11-13 | 2009-03-25 | 三一重工股份有限公司 | Control method and control device for driving hydraulic system of engineering vehicle by single pump and double motors |
| CN104653536A (en) * | 2015-01-15 | 2015-05-27 | 四川长江液压件有限责任公司 | Load sensitive valve |
| DE102014114210A1 (en) * | 2014-09-30 | 2016-03-31 | Claas Tractor Sas | Hydraulic control system |
| CN107143543A (en) * | 2017-04-27 | 2017-09-08 | 武汉船用机械有限责任公司 | A kind of hydraulic control valve group and control valve |
| CN207406559U (en) * | 2017-11-14 | 2018-05-25 | 浙江华益精密机械股份有限公司 | Torque distributing valve and wheel walking hydraulic control system |
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2017
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1309162A (en) * | 1969-06-28 | 1973-03-07 | Bosch Gmbh Robert | Fluid flow-regulating valves |
| CN101392774A (en) * | 2008-11-13 | 2009-03-25 | 三一重工股份有限公司 | Control method and control device for driving hydraulic system of engineering vehicle by single pump and double motors |
| DE102014114210A1 (en) * | 2014-09-30 | 2016-03-31 | Claas Tractor Sas | Hydraulic control system |
| CN104653536A (en) * | 2015-01-15 | 2015-05-27 | 四川长江液压件有限责任公司 | Load sensitive valve |
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Address after: 312000 Jiefang Road 689, Diankou Industrial Zone, Zhuji County, Shaoxing City, Zhejiang Province Applicant after: Zhejiang Huayi Precision Machinery Co.,Ltd. Address before: 312000 Jiefang Road 689, Diankou Industrial Zone, Zhuji County, Shaoxing City, Zhejiang Province Applicant before: ZHEJIANG HUAYI PRECISION MACHINERY Co.,Ltd. |
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